Side canal pump with a side canal located in the suction cover in order to avoid imperfect vortex structures

ABSTRACT

The invention relates to a side-channel pump having an intake cover ( 10 ), which is used in pumping fuel in a motor vehicle. The intake cover ( 10 ) has a side channel ( 11 ), extending radially about a pivot point ( 14 ) in the intake cover ( 10 ), a first opening ( 13 ) for an intake channel ( 27 ) of the side channel ( 11 ) and a constant side channel width (B SK ) in a portion extending circumferentially. The side channel ( 11 ) has a side channel width (B SK ) in the top side ( 8 ) that is constant, as seen from a beginning ( 12 ) of the side channel ( 11 ), already at a value of a first angle (φ) of between 0 and preferably approximately 5 and at most 20 , referred to a line (L B ) through the pivot axis ( 14 ) and through a contact point ( 1 ) at the beginning ( 12 ). This makes for better hot-gasoline performance, increased efficiency, and a higher pressure ratio of the side-channel pump. The intake cover is suitable in particular for a dual-flow side-channel pump.

BACKGROUND OF THE INVENTION

The present invention is based on a side-channel pump having an intakecover for a side-channel pump, which is used in pumping fuel in a motorvehicle. The intake cover has a side channel, extending radially arounda pivot axis in the intake cover, and also has a top side and anunderside and a first opening in the underside for an intake channel ofthe side channel. The fluid flowing through the side-channel pump flowsvia the intake channel through the side channel to an outlet from theside channel.

One intake cover and one design of a side-channel pump are known fromGerman Patent Disclosure DE 195 04 079 A1. An axially extending intakechannel discharges into a side channel that extends in the cover, inwhich side channel, as a result of pulse exchange events with a bladedrotor about its pivot axis, a pressure buildup takes place as far as theoutlet neck. The blading of the rotor is placed obliquely relative tothe pivot axis in such a way that toward one face end of the rotor it isleading in the circumferential direction of the rotor.

German Patent Disclosure DE43 43 078 A1 in turn describes a unit forpumping fuel by means of a side-channel pump. A side channel in anintake cover of the side-channel pump has a cross-sectional reduction bythe factor of 0.5, in order to act as a compression channel. Thiscross-sectional reduction extends over an angular range of approximately90 to 130 , referred to a beginning of the side channel; if there is alinear reduction in the cross section, then there is a transition via asmall step to the remaining constant side channel cross section. Aprogressive cross-sectional reduction contemplated there has acontinuous reduction in the side channel depth and side channel widthwithout any step. The cross-sectional reduction is than attained via areduction in the side channel depth and a progressive reduction, forinstance, in the side channel width over the angular range of 90 to 130.

SUMMARY OF THE INVENTION

It is therefore an object of the present invention to provide aside-channel pump which avoids the disadvantages of the prior art.

In keeping with these objects, one feature of present invention resides,briefly stated, in a side-channel pump, in which the side channel widthin the top side over an angular range having a first angle referred tothe reference line of 0 and 20 is constant as far as an outlet from theside channel.

The side-channel pump with an intake cover, as defined by the invention,has the advantage over the known prior art that the pump efficiency andhot gasoline performance are improved. To that end, the side channel hasa constant side channel width in the top side in the top side in anangular range having a first angle φ referred to a reference line, thatextends through the pivot axis and through a contact point at thebeginning of the side channel, of 0 , preferably approximately 5 , andat most 20 as far as the outlet from the side channel. Previously, theattempt had been made to avoid the formation of turbulence structuresthat cause loss and an unintended separation of the flow in the sidechannel by narrowing the side channel width steadily down to a constantvalue over a wide angular range. The proposed geometry, conversely,attains a higher suction level, for instance, because even at least inthe immediate vicinity of the beginning of the side channel, the sidechannel has the most constant possible width. The constant channelwidth, which as a result is disposed near the first opening for theintake channel, assures that in the region of an inlet flow of fuel intothe side channel, a development of braids of turbulence in the flow isavoided. Hydraulic losses and local negative pressure zones, which couldotherwise lessen the efficiency or, because of an increased vaporpressure in the case of hot gasoline in the summer could cause thedanger of cavitation and thus blockage of the blade cross section, aredecisively reduced.

It is also possible, because of the constant width of the side channel,that upon the inflow of fuel through the intake channel, a developmentof a detachment bubble, from the high suction occurring in an outerregion of the inflowing fuel in the case of a dual-flow side-channelpump, toward a pumping step located opposite the intake channel, issuppressed.

One advantageous refinement provides that the side channel has a centerline whose radius to the pivot axis remains constant, at the latestbeyond the first angle φ=15 . The center line is the line in the sidechannel that results when each width of the side channel is divided inhalf. The side channel as a result already extends circumferentially atthe intake channel without the imposition of an additional radial flowdirection on the flow as would be the case if the center line radiuswere not constant. As a result, an inlet flow pointing radially inwardtoward the pivot axis between the intake channel and the side channel isaverted. It is therefore advantageous for the center line radius toalready be constant at φ=0.

It is also preferred that the side channel have a constant width in thetop side no later than beyond the first angle φ=5. The side channelwidth is located in the face of the top side of the intake cover thathas the side channel which is open at the top. Below the top, or inother words between the top and the underside, the side channel in oneversion has a greater side channel width. However, this width preferablyalso drops, within at most φ=20 to 30 of the first angle, to theconstant side channel width in the top side. In this way, by a kind offunnel effect, a pressure buildup is again made possible, which has afavorable effect on the inflow of the opposed pumping step of adual-flow side-channel pump. In a further feature, this effect isreinforced by a transition from the first opening into the side channelvia the intake channel. The intake channel below the plane through thetop side has an increasingly slender transition that conforms to theside channel. This transition can already begin at the first, preferablyround opening. Below the underside, the side channel and the intakechannel with its transition therefore still have a greater width than inthe topside. This kind of favorable flow course is further promoted bythe fact that the first opening for the intake channel of the sidechannel, as well as the intake channel itself and the transition to theside channel, are designed to be as circular as possible.

It has proved to be a further advantage if an outer region of thebeginning of the side channel, with the most constant possible width,has an initial radius R_(A) relative to a side channel radius R_(SK) ofapproximate R_(A)=0.4 R_(SK) to R_(A)=1.1 R_(SK). The side channelradius R_(SK) is defined as the radius which maximally determines thegeometry of the side channel in the angular range of constant sidechannel width. This will be seen in more detail below from the drawing.A separation flow in the region of the beginning of the side channel isaverted by this kind of initial radius R_(A). At the same time, thismakes for a smooth transition of the inlet flow into the side channel,so that there is no disturbance to circulation with the attendanthydraulic losses. A further advantage of such a radius is that reverseflows are prevented. In that case, a blade chamber inflow into theblading of the side-channel pump is then unimpeded by collisions.

A development of turbulence braids in the inlet flow through the intakechannel at the transition to the side channel is also averted by theprovision that the first center point of the first opening is locatedradially closer to the dx than the center line along the side channel.Not only hydraulic but even local negative pressure zones are thusprevented, with the advantageous effects described above with regard tohot gasoline. A reduction in collision losses in the blade chamberinflow is also reinforced in cooperation with the first opening, locatedradially closer to the pivot axis, by the fact that the first centerpoint of the first opening is offset, by a second angle φ₂ of −5 to +15about the pivot axis relative to the reference line through thebeginning of the side channel, counter to a direction along the sidechannel. With the oblique blading of the rotor which is preferablyemployed, this makes for a uniform inflow of fuel into the bladechambers, because the axial and tangential speed components are morefavorable.

An especially advantageous feature of the intake cover has an additionalinner groove as a groove channel in the side channel. The groove channelprovides a continuous flow cross-section at the transition between theintake channel and the side channel. This is expressed in a uniformpressure buildup. The groove channel also enables a rapid and certaindissipation of any gas bubbles that may be present into a downstreamdegassing bore. A refinement of the groove channel provides that ittapers radially inward toward the pivot axis along an angular range φ₊about the pivot axis. Preferably, the angle φ for the range φ₊ isapproximately a value between 15 and 120 , and preferably 25 to 110 .This assures on the one hand that a calm, uniform transition of thegroove channel in the side channel is assured. On the other, thepressure buildup is also made uniform by a uniform tapering. The sidechannel can therefore be divided in this region along a width into oneregion of the groove channel and another region, which is the outerchannel.

To make the flow uniform, the groove channel has a depth which isgreater than that of the outer channel. For a steady transition and auniform pressure buildup, it is advantageous that the depth of thegroove channel decreases steadily. The development of turbulence fromtransition between flows of different radial, tangential or axial flowspeeds is maximally averted. Especially in cooperation with therevolving blade inlet edges of the blading, this steady transition leadsto a decrease in collision losses that would otherwise possibly occur.Making the fuel flow uniform in this way is attained in particular byproviding that a first groove bottom of the groove channel changes overinto a second groove bottom of the outer channel, and the two form acommon, homogeneous groove bottom of the side channel. These groovebottoms that merge gently with one another enable compression withoutthe hindering development of turbulence. On the contrary, anycirculatory flow that has built up and is intended in the side channelis brought to a developed state without hindrance in this way, whilereverse flows that involve loss are prevented. The buildup of thecirculatory flow is furthermore reinforced still further in that abeginning of the groove channel, in the region of the inflow of fuelthrough the intake channel, has rounded transitions.

An advantageous disposition of the groove channel in the side channelprovides that a radially inner boundary wall of the side channel is awall of the groove channel. As a result, an equalization of thedifferent speed components of the fuel flow flowing out of the intakechannel into the side channel is attained. At the same time, entrainedgas bubbles in this arrangement collect in the groove channel. Thedisposition of a degassing bore about a third angle φ_(*) ofapproximately 5 to 30 about the pivot axis relative to a tapered end ofthe groove channel in the side channel in the extension of the taperedend assures a rapid an reliable dissipation of the gas bubbles into thedegassing bore.

In accordance with a further advantageous concept of the invention,which in particular can also be realized in independent form, the intakechannel discharges obliquely into the first opening and into the sidechannel. This enables a radial inflow of fuel to the blading, whichgiven the addition of the vectorial speed components relative to theblading of the revolving rotor achieves a considerable reduction inhydraulic losses compared with a purely axial intake channel. Thereduction in hydraulic losses is reinforced by the fact that the firstopening has an opening radius R_(S) which is greater than the sidechannel radius R_(SK) by a factor of approximately between 1.75 and 3.5.The opening radius R_(S) is ascertained, given an approximately circularfirst opening, by abstracting a middle circle out of the contour of thefirst opening. The side channel radius R_(SK) is ascertained in asimilar way; it must be taken into account that the side channel has theside channel radius R_(SK) at the groove bottom. It has been found thatthe above-described advantages can be amplified decisively still furtherin a side-channel pump. The blade inlet edge and the first opening onthe underside, as an entrance for the fuel into the intake channel, havea spacing H_(S), which is greater by a factor of approximately between1.25 and 2.5 than the side channel radius R_(SK). This makes the inletflow uniform in the intake channel, and the transition to the blading iseffected in sliding fashion without any abrupt collision that wouldotherwise cause the development of turbulence.

In particular, the intake cover is suitable for a dual-flow side-channelpump. To that end, the intake cover with the side-channel pump has anopen side channel inflow cross section in the region of the beginning ofthe side channel for flooding a pumping step located opposite the intakechannel. The open side channel inflow cross section is preferablylocated in a region that is disposed between the first angle ofapproximately 5 to +40 about the pivot axis. The region can also bedescribed by means of a first, third and fourth reference point, as seenfrom the accompanying drawing.

DRAWING

One exemplary embodiment of the invention is shown in detail in theaccompanying drawing and explained in the associated description, inwhich further advantageous features and characteristics are described.

FIG. 1 shows a schematic plan view of a side channel in an intake coverwith a round first opening;

FIG. 2 shows three sections A—A, B—B and C—C along a width of the sidechannel of FIG. 1; and

FIG. 3 is a sectional view taken along the line D—D through the firstopening and through the side channel of FIG. 1.

EXEMPLARY EMBODIMENT

FIG. 1 shows a detail of an intake cover 10 in a plan view on a top side8. On the side opposite the topside 8, the intake cover 10 has anunderside 9, not visible in this view. The view shows a side channel 11.The side channel 11 has a beginning 12, which is disposed in a region ata first opening 13. Disposed in the beginning 12 is a first referencepoint 1, as a contact point, which as a starting point with a pivotpoint 14 defines a reference line L_(B) for a cylinder coordinate systemr-φ-z. The contour of the first opening 13, which is partly not visiblein this view, is suggested by dashed lines. Through the first opening13, in operation of the side-channel pump, the fuel flows through andinto a side channel, not visible in detail in this view. The firstopening 13 in this exemplary embodiment is a circle with an openingradius R_(S), whose first center coincides with a second reference point2. The side channel 11, which as it were extends out of the firstopening 13 via the intake channel, is disposed in a circular arc aboutthe pivot point 14. A pivot axis for a blading, not shown, of theside-channel pump therefore also extends through the pivot point 14.Also extending through the pivot point 14, perpendicular to the top side8, is a z-coordinate axis of the cylinder coordinate system. Thez-coordinate axis in this exemplary embodiment is coincident with thepivot axis of the blading. A center line 15 of the side channel 11 has acenter line radius R_(M) relative to the pivot point 14. The center line15 of the side channel 11 in this case corresponds to one-half of a sidechannel width B_(SK) of the side channel 11. In this exemplaryembodiment of the intake cover 10, half the side channel width B_(SK) isidentical to a side channel radius R_(SK) of the side channel, which inthe intake cover 10 defines an end cross section A_(SK) of the sidechannel 11. The width B_(SK) of the side channel is divided along thefirst angle φ into a groove channel width B_(NK) of a groove channel 16and an outer channel width B_(AK) of an outer channel 17. While the sidechannel width B_(SK) remains constant over the first angle φ, the groovechannel width B_(NK) varies, because it tapers downstream continuouslyalong an angular range φ₊ until a tapered end, which is identified as afifth reference point 5. There, a first boundary wall 18 of the sidechannel 11, which is at the same time a first boundary wall 19 of thegroove channel 16, coincides with a second boundary wall 20 of thegroove channel 16.

For further description of the geometry of the side channel 11, firstopening 13 and groove channel 16 in the intake cover 10, the referencepoints 1 through 7 will now be described, unless they have already beenlisted. Their coordinates are defined among other things as a functionof the side channel radius R_(SK), center line radius R_(M) along theside channel 11, and the opening radius of the first opening R_(S). Thethus-defined coordinates of the individual reference points 1 through 7are preferred for this particular application but can also deviate fromthis given a somewhat different geometry. In any case, it has proved tobe advantageous if the opening radius R_(S) is greater by a factor ofbetween 2 and 3 than the side channel radius R_(SK).

Reference Point r Coordinate Coordinate z Coordinate

Reference Point r Coordinate Coordinate z Coordinate 1 R_(M) 0 0 2R_(M) + R_(SK) − R_(S) −15° . . . +5° −(1.5 . . . 2.5 R_(S)) 3 R_(M) +R_(SK) 7.5° . . . 15° 0 4 R_(M) 15° . . . 30° −R_(SK) 5 R_(M) − R_(SK)90° . . . 120° 0 6 R_(M) − R_(SK) 15° . . . 30° 0 7 R_(M) − 0.5 R_(SK)15° . . . 30° −(1.5 . . . 2 R_(SK))

The coordinates of reference points 1 through 7 refer not only to FIG. 1but also to the coordinates of FIG. 2 and FIG. 3.

FIG. 1 shows that the beginning 12 of the side channel 11, the sidechannel has a constant width B_(SK) at reference point 1. In a preferredapplication of the intake cover 10 in a dual-flow side-channel pump, aninflow region 21 is designed such that the respective pump flows forflooding both pumping steps of the dual-flow side-channel pump aremaximally decoupled from one another. Flooding of the pumping step, notidentified by reference numeral here, remote from the first opening 13is effected in a region between the reference points 1, 3 and 4. To thatend, to avoid throttle losses, an inflow cross section, not shown here,to blade chambers not shown in FIG. 1 is designed to be open up to asecond boundary wall 22 of the side channel 11. In this case, this openinflow cross section extends over an angular range of the first anglethrough the first reference point 1 as far as the third reference point3. As a result, throttling upon flooding of the opposed pumping step inthe event of an overflow of the fuel is averted. An avoidance of thethrottling losses is additionally reinforced by providing an initialradius R_(A) at the beginning 12 of the side channel 11 whose size is afactor of between 0.4 to 1.1 of the side channel radius R_(SK) and byrecessing the second reference point 2, as the center point of the firstopening 13 by a second angle φ₂. The second reference point 2 isfurthermore located much closer to the pivot axis 14 than is the firstreference point 1 corresponding to the beginning 12 of the side channel11. The side channel width B_(SK) is less than the opening radius R_(S).

The circulatory flow necessary to increase the pressure is initiated byproviding that beyond reference point 3, the side channel 11 with theside channel radius R_(SK) is made continuously up to reference point 4in order to embody a groove bottom, to be described in further detailbelow, of the side channel 11. The aforementioned groove channel 16 inturn enables a continuous cross-sectional course of the inflow of fuelfrom the first opening 13 to the end cross section A_(SK) at referencepoint 5 of the side channel 11. The end cross section A_(SK) is shownshaded, using the side channel radius R_(SK). The geometry of the groovechannel 16 is defined largely on the one hand via an inner radius R_(IN)and on the other via a taper radius r_(v), which varies along an angularrange φ₊ along half the groove channel width B_(NK) from the pivot point14. The tapering radius r_(v) preferably extends linearly along areference line L_(NK) in the middle of the groove channel betweenreference point 7 and reference point 5 along a z-projection plane, inaccordance with the function$r_{V} = {{\frac{r_{5} - r_{7}}{\varphi_{5} - \varphi_{7}}\left( {\varphi - \varphi_{7}} \right)} + r_{7}}$

The inner radius R_(IN) of the groove channel 16 is preferably selectedas R_(IN)=r_(v)−(R_(M)−R_(SK)). The realization of the continuouscross-sectional course in the transition region between the firstopening 13 and the side channel 11 by means of the groove channel 16leads to a uniform pressure buildup as well as to a fast, reliabledissipation of gas bubbles into a down stream degassing bore 23. Thedegassing bore 23 is disposed away from the tapered end 5 by a thirdangle φ_(*) of approximately 5 to 30, and as shown the degassing bore 23extends downstream of the groove channel 16 and in the inner region ofthe side channel 11.

FIG. 2 shows three sections along the lines A—A, B—B and C—C of FIG. 1.The inner radius R_(IN) is defined such that a total side channel crosssection A_(GSK) composed of a channel groove cross section A_(NK) and anouter channel cross section A_(AK) in the line A—A through the fourthreference point 4, sixth reference point 6 and seventh reference point 7is greater by a factor of approximately 2 than the end cross sectionA_(SK) of the side channel 11 of FIG. 1. As can be seen from thesections B—B and C—C, the side channel cross section decreases along thefirst angle φ. This is preferably effected virtually linearly orslightly progressively; the end cross section A_(SK) of the side channel11 is reached at approximately the fifth reference point 5 in FIG. 1. Bymeans of this kind of tapering groove design, it is assured on the onehand that the outer channel 17 that has been made extends continuouslyinward, and thus the circulatory flow built up is not substantiallyimpeded. Second, gas bubbles can quickly be broken down by thedecreasing groove channel cross section A_(NK) and quickly carried awayto the degassing bore 23. In addition, a reverse flow that causes lossesis averted. A steady transition from a first groove bottom 24 of thegroove channel 16 to a second groove bottom 25 of the outer channel 17for forming a common, homogeneous third groove bottom 26 of the sidechannel 11, as shown in the three sections disposed one after the otherin FIG. 2, reinforces the avoidance of flow losses. This transition isindicated by the dashed reference line L_(NK), along which the innerradius R_(IN) of the groove channel 16 migrates steadily.

FIG. 3 shows a section along the sectional plane D—D in FIG. 1. Anintake channel 27 discharges into the first opening 13; the intakechannel 27 is oriented obliquely to the axially extending pivot axis 29of the rotor blades 30. The first opening 13 forms an inlet 28 for thefuel flowing into the side channel 11, as indicated by the arrow 31. Thefuel flows obliquely to the rotor blades 30, which means an oncomingflow with less impact and thus means a reduction in losses. Aninclination of the intake channel 27 to the pivot axis 29 is inparticular so marked that the second reference point 2 relative to thebeginning of the side channel, marked by the first reference point 1, isrecessed relative to the second angle φ₂ from FIG. 1. This obliqueinflow on the part of the fuel 31 is expediently exploited by the use ofrotor blades 30 that are also inclined by an angle β, adapted thereto,relative to the pivot axis 29. As already suggested by a course 32 alongthe reference line L_(NK) of the varying outset position of the innerradius R_(IN) through the reference point 7, a steady transition of thegeometries for the inflowing fuel 31 is also attained by means ofrounded transitions 33. The geometry of the intake cover 10 is alsoespecially well suited for a dual-flood side-channel machine, notidentified by reference numeral, with an unthrottled overflowperformance at a parting rib between the blade chambers disposedopposite one another. It is preferred if a spacing H_(S) between theinlet 28 into the intake channel 27 and an inlet edge 34 of the bladehas a value that is greater by a factor of approximately 1.3 to 2.8 thanthe opening radius R_(S) of the first opening 13. With this kind ofdimensioning, collision losses upon the inflow of fuel 31 are extremelyslight.

What is claimed is:
 1. A side-channel pump for fuel pumping in a motorvehicle, having an intake cover (10) with a top side (8) and anunderside (9), a tapering side channel (11), open on the top side (9)and extending circumferentially about a pivot point (14) of theside-channel pump, a first opening (13) in the underside (9) for anintake channel (27) of the side channel (11), the intake channel (27)extending from the underside (9) to the top side (8), and a side channelwidth (B_(sk)) that is constant at least in the top side (8), at leastin a portion extending circumferentially, and a reference line (L_(B))extends through the pivot axis (14) and through a contact point (1) atthe beginning (12) of the side channel (11), the side channel width(B_(sk)) in the top side (8), over an angular range having a first angle(φ), referred to the reference line (L_(B)), of 0 and 20, is constant asfar as an outlet from the side channel (11), and additional internalgroove in the form of a groove channel (16) assigned to said sidechannel (11).
 2. The side-channel pump of claim 1, wherein the sidechannel (11) has a center line (15), whose center line radius (R_(M))from the pivot axis (14) remains the same at least beyond the firstangle ( ) of approximately
 15. 3. The side-channel pump of claim 1,wherein the side channel (11), at least beyond the first angle (φ) whereφ=5 in the top side (8) has a constant side channel width (B_(SK)),while below the top side (8), the side channel width (B_(SK)) of theside channel (11) is even greater.
 4. The side-channel pump of claim 3,wherein below the top side (8), the side channel width (B_(SK)), withinthe first angle (φ) of at most =30, tapers down to the constant sidechannel width (B_(SK)) in the top side (8).
 5. The side-channel pump ofclaim 1, wherein the beginning (12) of the side channel (11) in an outerregion has an initial radius (R_(A)) relative to a side channel radius(R_(SK)) of approximately R_(A)=0.4 R_(SK) to R_(A)=1.1 R_(SK).
 6. Theside-channel pump of claim 1, wherein a first center point (2) of thefirst opening (13) is offset by a second angle (φ₂) of −5 to +15 aboutthe pivot axis (14) relative to the beginning (12) of the side channel(11), counter to a direction along the side channel (11).
 7. Theside-channel pump of claim 1, wherein an intake channel (27) dischargesobliquely into the side channel (11).
 8. A side-channel pump for fuelpumping in a motor vehicle, having an intake cover (10) with a top side(8) and an underside (9), a tapering side channel (11), open on the topside (9) and extending circumferentially about a pivot point (14) of theside-channel pump, a first opening (13) in the underside (9) for anintake channel (27) of the side channel (11), the intake channel (27)extending from the underside (9) to the top side (8), and a side channelwidth (B_(sk)) that is constant at least in the top side (8), at leastin a portion extending circumferentially, and a reference line (L_(B))extends through the pivot axis (14) and through a contact point (1) atthe beginning (12) of the side channel (11), the side channel width(B_(sk)) in the top side (8), over an angular range having a first angle(ψ), referred to the reference line (L_(B)), of 0 and 20, is constant asfar as an outlet from the side channel (11), the side channel (11) hasan additional internal groove in the form of a groove channel (16). 9.The side-channel pump of claim 8, wherein the groove channel (16) tapersradially inward around the pivot point (14).
 10. The side-channel pumpof claim 9, wherein the groove channel (16) tapers along an angularrange (₊) about the pivot point (14) having the first angle (φ) ofapproximately or equal to 15 to 120, preferably 25 to
 110. 11. Theside-channel pump of claim 8, wherein the groove channel (16) has adepth which is greater than that of an outer channel (17) of the sidechannel
 11. 12. The side-channel pump of claim 8, wherein the depth ofthe groove channel (16) increases steadily.
 13. The side-channel pump ofclaim 8, wherein a first groove bottom (24) of the groove channel (16)changes over into a second groove bottom (25) of the outer channel (17),and the two form a common, homogeneous third groove bottom (26) of theside channel (11).
 14. The side-channel pump of claim 8, wherein aradially inward-located boundary wall of the side channel (11) is a wallof the groove channel (16).
 15. The side-channel pump of claim 8,wherein a degassing bore (23) is disposed at a third angle (φ_(*)) ofapproximately 5 to 30 about the pivot point (14) in reference to atapering end (5) of the groove channel (16) in the side channel (11) inthe extension of the tapered end (5).
 16. The side-channel pump of claim1, wherein the first opening (13) has an opening radius (R_(S)), whichis greater by a factor of approximately between 1.75 and 3.5 than theside channel radius (R_(SK)).
 17. The side-channel pump of claim 1,wherein a spacing (H_(S)) between a blade inlet edge (23) and an inlet(28) for the fuel (31) into the intake channel (27) is greater by afactor of approximately 1.25 and 2.5 than the side channel radius(R_(SK)).
 18. The side-channel pump of claim 1, wherein as a dual-flowside-channel pump, it has an open side channel inflow cross section in aregion between the first reference point (1), the third reference point(3), and the fourth reference point (4), for flooding a pumping steplocated opposite the intake channel (27).
 19. An intake cover (10) for aside-channel pump having an embodiment according to claim
 1. 20. Aside-channel pump for fuel pumping in a motor vehicle, having an intakecover (10) with a top side (8) and an underside (9), a tapering sidechannel (11), open on the top side (9) and extending circumferentiallyabout a pivot point (14) of the side-channel pump, a first opening (13)in the underside (9) for an intake channel (27) of the side channel(11), the intake channel (27) extending from the underside (9) to thetop side (8), and a side channel width (B_(sk)) that is constant atleast in the top side (8), at least in a portion extendingcircumferentially, and a reference line (L_(B)) extends through thepivot axis (14) and through a contact point (1) at the beginning (12) ofthe side channel (11), the side channel width (B_(sk)) in the top side(8), over an angular range having a first angle (ψ), referred to thereference line (L_(B)), of 5 and at most 20, is constant as far as anoutlet from the side channel (11), the side channel (11) has anadditional internal groove in the form of a groove channel (16).